Liquid pump



March 21, 1933. s. wl TRAYLOR, JR

LIQUID PUMP Filed May 19, 1952 Wpc ov M ma@ m@ JW 3 5. 0 c wel w au@ n J y Sama ' thevalve and toggle spring assembly in the f by the greatest pressure likely to be enc-oun Patented Mar. 21, 1933 UNITED STATES PATENT fori-ICE SAMUEL W'. TRAYLOB, JR., `OIE ALLENIOWN, PENNSYLVANIA, ASSIGNOR TO TR-AYLOR ENGINEERING MANUFACTURING COMPANY,

CORPORATION 0F DELAWARE I .Application l'ed May 19,

This invention relates to liquid pumps oli that type operated by high pressure gas or air, and has for one of its objects to provide a pump of this character adapted for single tered in the working chamber. y

To attain the foregoing and other objects, the natureof which will appear as the description proceeds, the invention comprehends apump wherein the valve operating mechanism will include means lconstantly tending to move the valve into pumping position, and a weight acting to shift thevalve into filling position when the liquid in the operating or working chamber is reduced to a predetermined level, the downward force of the'weightbeing lessened suiii'ciently to permit said means to shift the valve to pumping position when the liquid in the chamber rises to a predetermined level, the weight atA all times exerting a downward force on the rest of the valve operating mechanism. .Y y

V The kinvention is hereinafter fully described, and claimed, and diagrammatically illustrated in the accompanying drawing, wherein:

Figure l is a diagrammatic vertical sectional view of a pump embodying my iii-- vent-ion, the valve of the pumpbeing shown in pumping position, and n Fig. 2 is a similar view of the pump with the valve. in filling` position. Y

Fig. 3 is an enlarged fragmentary view oi.

position of Figure l.

The amount of `movement. of the valve stem and of the opening" and closing of the passage'l to the top of thewell.

OF ALLENTOWN, PENNSYLVANA, A

LIQUID PUMP 1932. serial No. 612,348.A

valvesis actually quite small, the drawingl being, -for thev purpose lof clear illustration, somewhat exaggerated.

Referring in'detail'to `the drawing, l designates an outer and 2 an inner casing of the pump; 'The casing 1v is provided with a foot valve, and secured to the upper end of this casing isa valve and coupling block 4. A pipe 5 extends from the' block` 4to pipe 5 is connect/edito the next highest stage.

the. top .ofthe 'well when but one stage is usedl It two or more stages are used, the

rl`he block 4 is provided with passagesl 6 through which the liquid being pumped flows from the outer casingl into the pipe 5.V Downflow through the pipe 5 is prevented by a ball check valve 7 located in the v pipe immediately above the'bloclr 4.

The inner vcasing 2 has vits upper end se'- cured, as at 8, to the block 4, and is 'spaced from the outer. casing to provide an annular low passage 9 which extends from the foot i lupper seatslv of the valve face-upwardly,

and the lower seats 14 of .the valve face downwardly. f An inlet passage .15 for the operating medium extends from the upper end ofthe block 4to aV chamber 13a located between the valve seats 13. A .discharge passage lprfor the operating medium ex-VV tends to the upper end'of the block 4 from a chamber 14a located between the valve seats 14. A tube117 conveys the operating rne-v dium to the passage 15, and a. tube 18 conveys the exhaust operating medium from the tudinal passage 19, communicating with the A longichambers 13a and 14d above andbelow the lm valve ser ts, serves in one position of the valve to convey the operating medium from the chamber 13a to the passage 12, and serves in another position of the valve to convey the operating medium from the passage 12 to the chamber 14a.

A stem 20, extending through the passage 12, and through the seats 13 and 14, is provided with, heads 13;?) cooperating with tl e seats 13 and with heads 14?; cooperating with the seats 14. The downward movement of the valve stem 2O seats the valve heads 13b and unseats the valve heads 14?). When the valve is in this position (Fig. 2), communication between the inlet passageV 15 and the working chamber 2`is cut off, and communication between the working chainber and the exhaust passage 16 is established. As the operating medium is not flowing tothe working chamber 2,.and as the exhaust of the working chamber is open, the liquid in which the pump is immersed will flow into the working chamber. i During the inflow of the liquid, the exhaust operating medium flows from the working chamber by way of the passages 12 and 19, chamber 14a and passage 18. The upward movement of the valve stem 2O unseats the valve heads 13?) and seats the valveheads 14?). When the valve is in this position (Fig. 1), communication between the inlet passage 15 and the working chamber is cstablished, and communication between the working Ychamber and the exhaust passage 1G is cut off. As the operating medium is now flowing to the working chamber 2, and as the exhaust of the working chamber is closed, the liquid in the working chamber is being forced therefrom by the high pressure gas or air, the liquid flowingfrom the working chamber into the passage 9v by way of the ports 11, and the liquid flowing from this passage through the passages 6 and pipe 5. The liquid passes through pipe 5 to the top of the well or to the next stage above directly into the casing 1 of such ne): stage beneaththe closed. bottom 10 of the casing 2 thereof. The operating medium Hows from the tube 17 to the working chamber 2 by way of the passage 15, chamber laand passages 19 and 12.

The pressure receiving area of the lower head of the inlet pair 13h-is suiiiciently yadapt themselves to crooked i wells.

larger than the pressure receiving area of the upper inlet head so that the incoming pressure will, when these heads are seated, hold the valve in this position (Fig. 2). As the valve when in this position permits the liquidv in which the pump is immersed to flow into the working chamber, this position of the valve is hereinafter referred to as the lling position. This overbalancing is not great enough to interfere Ywith breaking the seal bythe operating mechanism for the valve, as hereinafter described.

The valve operating mechanism comprises a weight 21 vwhich is located in the working chamber 2vand which is connected to the valve stem 20 by a rod 22. The weight 21`is' of sectional formation, and the sections or parts 21a thereof areconnected by rod connections23. The rod connections between the weights are flexible enough to These connections are spring steelrods that will bend a goodvdeal before breaking, and they always come back to their original position. It must be remembered also that wells are never so crooked within a distance of the length of the filling chamber (which would ordinarily be within SO) that the rods would not adapt themselves. rlhese connecting rods provide resilient or flexible means that normally tend to hold the weights all in line. kThis means that the weights at all times have-a tendency to have their axis lparallel to the'aXis of the working chamber, thereby obtaining the most benefit from the fluid splitting ends of the weights. If the axis of the weights should be permitted to become non-parallel with the axis of the chamber, this would present an inclined broa'dside of the weight to the action.of the liquid rushing Vup and down which would naturally interfere with operation. Y

The weight sections 21a are preferably of elongated cylindrical formation, and are considerablyV smaller diametrically than the working chamber 2. The weight sections 2101, the embodiment illustrated, are ar-V ranged at oppositesides of the transverse center of the working chamber 2, two of the weight sections beingl located in the Yupper and two in the lower portion of the working chamber. Any number of weights or weight sections may be used, four weights as shown, being usually suiiicient to operate a pump, and in order to get volume or cagpacity, the lling chamber should beof AvI tay

25 isf sleeved: on therod 22 with its: lower vUnder conditions hereinafter set forth, the

weight 21 acts to move the valve stem 2() downwardly to close the inlet passage andopenthe exhaust passage 16, and thus move the valve from its p umpingV vto its filling position..v Under conditions hereinafter set forth, the spring 25 acts to move the valve stem upwardly to-open the inlet passage 15 and close the exhaust passage 16, andthus move the valve from its filling to its pumping position;

The upper end of the rod 22 fits in the forked lower end of the valve stem 20. These ends have, as sho-wn at 27, a pin and slot connectionso that the rod 22 may move upwardly and downwardly for a limited distance without moving the valve stem 20. After the downwardmovement. of the rod and weightsI 22 for` this limited. distance, toggle springs 28 act to effect the-instantaneous movement of the valve from-its pumping to its filling position, .and after the. upward movement ofthe rod and weights for this limited distance, these springs act to effect the instantaneous movement of the valve from its filling to its pumping position.

These springsvhave knife edge ends 28a, and

28Z Lengaging corresponding grooves in: opposite sides of the rod 22I and grooves 1n slightly cambered bearing members 29 'recessedin adpistable screw plugs i3() in.'` the casing 24.v The springs V28 extend upwardly when the valve is in pumping position, as shownL in Figure 1. The* :springs extend downwardly when the valveis 1n filling position, asA shown in Figure 2. The springs V28ers moved past dead center from one of their inclined positions by the rod 22during the limited movement of the rod with relation to the valve stem` 20. The springs 28 are under initial tension and exert sufficient power to-quickly move the slightly overbalancedv valve stem -from one of itspositions tothe other after slight movement beyond Vdead center. Y y' The weight 21 functions to effect the movement ofthe valve from'o'ne of its posi-Y tions to the other on the principle thatevery body immersed in a liquid is submitted to the actions oftwo forces.; namely,- gravity, which'tends to lower it, and the buoyancy 'of thefliquichwhich tends to: raise it withy a l force; equaltothe weight of, the liquid'dis.- i

placed. It therefore follows that the dow-n- .ward force of the weight;l 21 will; decrease downward force of the weighty -e'ffectsvthe movement of the valve from its pumping to its fillingV position. When. the valve isfin filling posi-tion, theinlet passage 15 is closed andthe exhaust passage 16'isv open, the

spring 25, being subject to the gravitational 5 force of the weight 21, sunder compression, and the toggle springsl 28v incline downwardly, as shown in Figure 2. When the liquid flowing into theY passage 9 and` into the working ehamber2 rises to a predeterj mined level, such as.arbitrarily'indicated in Figure 1, the downward force of the weight 21 will vbe reduced by the buoyancy ofv the liquid lsuficiently to permit the spring 25 to i react and move the weight and therod 22 upwardly against the action of .toggle springs 28.A During the first phase of its upward movement,.the. rod 22 will, due to its pin-and slot connection 27 with the-valve A stem 20, move with relation to the valve stem, and carry thel toggle springs 28 past their dead center.r Immediately after the springs 28 khave been moved past their dead center they will, as all lost motion between Vthe link 22 and valve stem 20 has been taken up, act in conjunction withthe spring '25 to quickly shift the valve from filling topumpingpositionfWhen the valve is in pumping Vposition the inletv passage 15 is open, the

exhaust passage 16 is closed', and thel toggle springs incline upwardly. The incomingoperating medium-high pressure gas` or airforces the liquid in the working chamber 2 through the ports 11 into fiow passage), the liquid flowing from this passage through the passage 6 to and through the' pipe 5 to the top of the well, V4or to the next highest stage of thepump, depending upon whether one or more stages are used. When the level of the liquid in workingv chamber2'7is. re

duced to. a, predetermined level, suchV as larbitrarilyfindicated in Figure 2,*the downward force of the weight Y21will be increased suflicientl'y to cause it tomove down- .E wardly against the tension of thel springs 25 and slot connection V27 with the valve stem` 20, move with relation tothe valve stem and.

carry the toggle springs 28 past their` dead center. Immediately after the springs 2 8 have been moved past their dead centerfthey will,v as all lost motion between the link V22 and valve stem 20 has been taken up, actin conjunction with the weight 21 to quickly Vshift the valve from pumping to filling in the working chamber 2 falls to a predetermined low level, and the downward force of the weight, combined with the downward force exerted by springs 28, will not become less than the upwardforce of the spring 25 until the liquid reaches a predetermined high level in the working chamber.

For example, assuming that the weight at a particular rising level of liquid while the pump is filling, exerts a downward gravitational force of 1() lbs. Assume that thisv is balanced by a net upward force of lbs.,

-being the difference between the upward force of the operating spring of 50 lbs. and the downward force of the toggle ksprings of lbs. With this balanced con dition, a further rise of liquid level will reduce Athe downward force of the weight slightly, `which will permit the operating spring to move the rod 22 and the weights up until the dead center of the toggle springs is passed when they quickly actuate the valve by exerting their force upwardly.

By way of further illustration, assuming that the weight at a particular decreasing level of liquid while the pump is pumping, exerts a downward force of lbs., and that this is balanced by 40 lbs. exerted upwardly by the toggle springs and 10 lbs. exerted upwardly by the extended Yopera-ting spring. With this balanced condition, a further .decrease of liquid level will increase the dow-nward .force of the weight slightly, which will move the rod 22 downwardly until the dead center of the toggle springs is passed when they quickly actuate'thc valve by exerting their force downwardly. The f`1gures given are purely illustrative and the invention isin no wise to be limited thereto.

The levels as illustrated in the drawing,

yare merely arbitrary and for illustration only, and are not to be construed as limiting the levels to any .particular points in the length of the working chamber@ In order to prevent the rushing motion of liquid Vflowing into and out of the working chamber 2 fromV imparting any axial motion tothe weight 21, and thus insure the shifting of the valve solely as the result of variations in the buoyancy oft-he weight, (i. e. as the result ofvvariations inthe effective downward force of the weight on the valve control assembly including the spring 25) the lowermost of the upper weight sections 21a is `provided at its lower end withl a. cone lor taper 33, and the uppermost of the lower weight sections isfprovided at its upper end with a cone 34. The cones or tapered ends split thefinflowing and outiowing streams sections.

ofliquid and thus prevent their imparting axial movement to the weight and prevent premature shifting of the valves. As shown, the cones 83 and 34 are in the'form o f attached shields, butV it will be apparent that they may be yformed integral with the weight That the cones or tapered ends may be employechif desired, in connection with all of the ends of the weights, will be apparent. The plate 10 Awhich closes the lower end of the workingl chamber 2 answers the same purpose for the incoming oil. This plate splits the inrushing oil `and makes it enter the inner chamber through slots 11, thereby preventing the weights from being washed up and shifting the valve prematurely. Y f

The weight 21 is made from non-magnetic metal to the end that it may function eiliciently in wellshaving high residualmagn netism, it beinO' an object of the invention to provide non-magnetic buoyant means for the operation of pumps. Some oil wells have a high residual magnetism, and the use of ferrous or other magnetic floats or weights as the buoyant actuating means for the .valves is impractical lin magnetic wells, as this magnetism will hinder the successful operation of the buoyant means. Aluminum weights have been found by experiment to operate successfully in magnetic wells such as are encountered in California.

The weight 21 is of sectional formation in order to prevent the ccolumn effect encountered in high pressures bending or otherwise damaging it, and to provide for lateral flexibility when operating in crooked wells. The weight 21 is long and slender to adapt it to be used in small diameter wells and to function eliciently in crooked wells.

A buoyant member used as an operating means in an oil well must of necessity be long` and slender. It must have Vlength in order to give it volume, and it must be slender to adapt it for use in oil wells, the casings of which are sometimes as small as Y a in diameter.

A buoyant member in well pump, to operate high 'pressure valves and overcome friction of the moving parts, as well as the friction between the buoyant member and its housing (particularly in crooked Iwells) must have considerable volume, as lthe volume of liquid displaced by the .buoyant means is a measure of the buoyant effort `available for the voperation ofthe pump.

A buoyant member having sufficient volume for the operation of a pumpv becomes Vtoo long for practical use when high pressures are encountered unless itis sectionallzed; i. e., 1n several parts.

The reason for this is that a long, slender buoyant member has the high pressure acting on its ends, and this end pressure produces a column effect in 'the buoyant member and causes it torbend or break intermediate its. ends and this renders it useless. Bending causes the buoyant member to bind in its working housing and thereby renders it useless for the Voperation of the pump. If, as in the present inve-ntion, the buoyant member is made in several pieces and the pieces'short enough to withstand the column effect of the pressure under which they work, Vthese diculties are overcome. Y

The. weight 2l functions more efficiently than a float, especially in high pressures, for

the reason that a float made strong enoughv to withstand high pressuresV would be so heavyV that its useful buoyancyV is insuflicient VVl for satisfactory operation of the valves.

The invention provides a valve structure in a well pump that has no sliding contacts, thereby-eliminating friction, and also eliminating the `need for lubrication; This is very important as when natural gas is used for the operation of a pump, the gas renders any bearings or sliding contacts extremely dry, and, therefore, increases the friction in the valve structure to such an extent that successful opera-tion is questionable and in some cases'impossible.

A- feature of the present invention is that a downward force is at all times exerted on the valve operating or control mechanism by 'the buoyantly vcontrolled member or weight, also referred to herein and in the claims as a buoyant member or members.

Floats cannot be used when their buoyant force alone must operate a valve, because under high pressure floats must be made so heavy to withstand pressure that the buoyant .effect available is very small, whereas with a weight the buoyant effect can be verymuch greater, inasmuch as the excess weight of a weight overthat of a float is counterbalanced, this excess weight being counterbalanced by a spring, as shown,`or by another weight, or by any other means. The weights must always exert a downward force against the counterbalancing force. This construction tends toward improved stability and accuracy of operation as distinguished from floats.

Ioclaim:

1. In a liquid pump, aworking chamber,

valve means controlling motive fluid inletV and exhaust for said chamber, operating means'constantly tending to move said valve means into inlet position, and a buoyant member located in said chamber and constantly exerting a downward force tending to move the valve means into exhaust position, :said buoyant member being adapted when the liquid in said chamber is reduced to a predetermined low level to positively move said valve means intov exhaust position against the -force of said operating means, said buoyant member having its which said operating means comprises a spring constantly tending to move said valve means upwardly against the gravitational 'force of said weight.

3. In a liquid pump, a working chamber, valve means controlling motive fluid` inlet and exhaust for said chamber, and means for operating said valve means, said operating means including a weight located in said chamber and having its downward force varied by the rise and fall of the liquid in said chamber to effectthe operationof vsaid valve means, said operating means including Vvthe weight being .in substantial longitudinal alignment for a substantially frictionlessline motion directly from the buoyant force of the liquid on the weight to the valve.

means, said motion.

t. In a liquid pump, a working chamber, valve meansv controlling motive liuid inlet and exhaust for said chamber,-and means for operating said valve means, said operating means including a weight located in said chamber and exertingat all times a downparts being free from rotary ward force on the rest of the valve operating means, said `weight having its downward force varied by the rise and fall of the liquid in said chamber to effect the operation of said valve means', said valve operating means i also including a rod connecting the said weight with the valve stem, a spring oonstantly tending to move the ro'd upwardly,

and toggle spring means to actuate said rod in conjunction with said weight and spring.

5. In aliquid pump, a working chamber,-

valve means controlling motive fluid inlet and exhaust for said chamber, and means for operating said valve means, said operating means including a weight located in said chamberand exerting at all times a down-` ward force von the/rest of the valve operating means, said weight having-its downward force varied by the rise; and fall of the liquid in said chamber to effect vthe operation of said valve means, said valve operating means also including 'a rodconnecting the said weight with the valve stem, a spring constantly tending to'move the rod upward-` ly, toggle spring means to factuate Vsaid rod in conjunction with said weight and spring, and a lost motion connection between the end of the rod and the valve stem to provide for positive and instantaneous action of the toggle springs 'upon the valve stem when their dead center is passed.

6. Apparatus according to claim 1 in which said means comprises a spring constantly tending to move said valve means upwardly against the downward force of said buoyant member, said valve and operating means including the buoyant member and spring being in longitudinal alignment for a substantially frictionless line motion directly from the buoyant force of the liquid on the buoyant member to the valve means, said parts being free from rotary motion.

7. In a liquid pump, a working chamber, valve means controllingvmotive fluid inlet and exhaust for said chamber, and means for operating said valve means, said means including a weight located insaid chamber and having its downward force varied by the rise and fall of the liquid in said chamber to elfect the operation of said valve means, saidweight comprising upper and llower weight sections with laterally flexiblev connections therebetween, normally tending to hold the weight sections all in line and axially parallel or coincident with the axis of the working chamber.

8. In a liquid pump, a working chamber, valve means controlling motive fluid inlet and exhaust for said chamber, and means for operating said valve means, said operating means including .a weight located in said chamber and having its downward force varied bythe rise and fall ofthe liquid in said chamber to collect the operation of said valve means, said weight comprising an upper pair of adjacent weight sections and a lower pair of adjacent weight sections and longitudinally rigid connections between said I weight sections, the connection between said pairs being laterally llexible and resilient, said connect-ions normally tending to hold the weight sections all in line and axially parallel or coincident with the axis of the working chamber.

9. Apparatus according to claim 7 in which said upper and lower weight sections are disposed on opposite sides of the transverse center of the length of the weight, and tapered ends provided on the weight sections to. provide a streamline effect preventing premature' movement of the weight by the rush of liquid into and out of the working chamber. Y Y

10. In a liquid pump, a working chamber, valvemeans controlling motive fluid inlet and exhaust for said chamber, and means for operating said valve means, Vsaid operating means including a weight located in said chamber and exerting vat, all timesa downward force on the rest ofthe valve operating means, said weight having its downward force varied by the rise and fall of the liquid in said chamberto effe-ct the operation of said valve means, said weight comprising Yupper andV lower weight sections with connections therebetween, and fluid splitting means provided on the ends of the weight sections to preventpremature movement of the weight by the rush of liquid.

11. In a liquid pump, a working chamber, valve means controlling motive fluid inlet and kexhaust for said chamber, operating means constantly tending to move said valve means into inlet position, and a weight located in said chamber and adapted when the liquid in said chamberl is reduced to a predetermined low level to move said valve means into exhaust position against the force of said operating means, said weight having its downward force reduced by thev liquid when it rises to a predetermined high level in saidchamber to permit-said valve means to be moved by said operating means into inlet position, said. valve means'comprising a pair of valves controlling admission Vof motive fluid and a pair of valves controlling vent or exhaust of motive fluid, said valves all being mounted in line on a commonstem.

12. Apparatus according to claim 11 in which the valves of each pair have dilfere'ntial Vpressure receiving Vareas to maintain them normally seated. l

13. In aliquid pump, a working chamber, valve `means controlling motive fluid inlet and exhaust for said chamber, and means for operating said valve means, said Yoperating means including a weight located in said chamber and exerting at all times a downward force on .the rest of the valve operat- 'ing means, said weight having its downward force varied by the rise and fall of the. liquid in said chamber to effect the operation of said valve means, said valve operating means also includinga rod connecting the l said weightwith the valve stem, a spring constantly tending to move the rod upwardly, toggle spring means to actuate said rod in conjunction with said weightl and spring, and a lost motion connection between the end of the rod and the valve stem to provide for positive and instantaneous action of the toggle springs upon the valve stem when their dead center is passed, said valve means comprising a pair of valves controlling admission of motive fluid anda pair of valves controlling vent or exhaust of motive lluid, saidvalves all being mounted in line on a common operating stem, andthe valves of each pair having differential pressure receivingv areas to maintain them seated normally. f

14. In a .liquid pump, a valve block, valves in said block controlling motive fluid inlet and exhaust, an outer casing, an. inner casing forming with the outer casing a discharge conduit for liquid being pumped from the casing through lthe valveblock, a weight within said inner casing, a third casing depending from said valve block, a rod,

extending' upwardly from said weight and guided in the lower end of Said third casing, ports in said casings to provide for entrance and egress of motive fluid and of liquid being pumped and a connection between said rod and valves to operate the valves.

l5. Apparatus according to claim lll in which a pair of motive fluid inlet valves and a pair of motive fluid outlet valves are provided in line on a common operating stem, a motive fluid inlet port in the valve block leading to a chamber between the two inlet valves, chambers above and below said inlet valves each communicating witha vertical passage to the open lower end of the valve block, a motive fluid outlet port leading to a chamber between the two outlet valves, ports in saidV third casing communicating the lower open end of the valve block with the interior of said inner casing, and a port through the valve block from said discharge conduit for upward discharge of pumped liquid.

16. Apparatus according to claim 14 in which said connection includes a valve stem common to all of the valves, a lost motion connection between said rod and valve stem, toggle springs engaging grooves in the rod and in the said third casing, and a spring adjustably seated on the third casing and engaging said rod to urge the same upwardly.

17. Apparatus according to claim 14 in which said weight is of elongated sectional formation, including conical ends provided on the weight sections, said inner casing having its lower end sealed and provided with ports in its wall for passage of liquid to prevent the rush of liquid into and out-oi the pump from prematurely moving the weight. Y Y

18. In a liquid pump according to claim 1, said buoyant member acted upon by the buoyancy of the liquid for operating said valves being of non-magnetic material.

19. Apparatus according to claim 7 in which said weight is constructed and arranged to exert at all times a downward force on the rest of the valve operating means.

20. Apparatus according to claim 7 in which said weight is sectionalized, each section being sufficiently strong as a column to resist the force affecting it as a column, said force being caused by the pressures to which it is subjected.

In testimony whereof I aliiX my signature.

SAMUEL W. TRAYLOR, J R. 

